EP1360100B1 - Master cylinder comprising a fluid and replenishing seal - Google Patents

Master cylinder comprising a fluid and replenishing seal Download PDF

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Publication number
EP1360100B1
EP1360100B1 EP02704796A EP02704796A EP1360100B1 EP 1360100 B1 EP1360100 B1 EP 1360100B1 EP 02704796 A EP02704796 A EP 02704796A EP 02704796 A EP02704796 A EP 02704796A EP 1360100 B1 EP1360100 B1 EP 1360100B1
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EP
European Patent Office
Prior art keywords
piston
master cylinder
seal
bore
pressure chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02704796A
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German (de)
French (fr)
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EP1360100A1 (en
Inventor
Juan Simon Bacardit
Bruno Berthomieu
Fernando Sacristan
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Sistemas de Frenado SL
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Bosch Sistemas de Frenado SL
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Publication of EP1360100A1 publication Critical patent/EP1360100A1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
    • B60T11/16—Master control, e.g. master cylinders
    • B60T11/236—Piston sealing arrangements

Definitions

  • the invention relates to a brake master cylinder for a motor vehicle.
  • the invention relates more particularly to a brake master cylinder for a motor vehicle, of the type which comprises a substantially axial body within a bore of which is slidably mounted at least one axial piston, which can be actuated by a driver of the vehicle between a rear position of rest and a position before application of a braking force, and which is resiliently biased towards its rear rest position against a stop formed in the body, the a type in which the bore has two front and rear sealing means which are interposed between the piston and the bore, the front sealing means defining in the bore a rear supply chamber and a front pressure chamber, of the type in which the body comprises a radial supply duct which connects an external reservoir of hydraulic fluid to the rear supply chamber and which opens out between the two means of supply.
  • sealing of the type in which the body comprises a feed hole of a braking circuit which opens into the front pressure chamber, of the type which comprises means for communicating the front pressure chamber and the chamber which are likely to be inhibited by the piston when it is moved axially forward towards its application position to isolate the front pressure chamber of the rear feed chamber and thus allow the establishment a braking pressure in the front pressure chamber.
  • At least one of the two sealing means is carried by the piston. It is therefore subject to significant wear due to the reciprocating movements of the piston in the bore of the servomotor body during successive braking.
  • the invention provides a brake master cylinder of the type described above, which comprises at least one seal carried by the bore of the body.
  • front and rear respectively designate elements or positions respectively oriented to the left and right of the figures.
  • the master cylinder 10 is a "tandem" type master cylinder which comprises a substantially axial body 12 of axis A inside a bore 14 of which are slidably mounted two axial pistons 16 and 18.
  • master cylinder 10 could be a simple master cylinder having only one sliding piston.
  • the piston 16, said primary piston 16, is intended to allow the establishment of a hydraulic pressure in a primary braking circuit of the vehicle (not shown), and the piston 18, said secondary piston 18, is intended to allow the establishing a hydraulic pressure in a secondary braking circuit of the vehicle (not shown) which is independent of the primary brake circuit of the vehicle.
  • the primary piston 16 can be actuated directly by a driver of the vehicle.
  • a rear end 19 of the primary piston 16 may be connected to a servomotor (not shown) which amplifies the forces exerted on a brake pedal of the vehicle.
  • the secondary piston 18 may be actuated indirectly by the driver of the vehicle, in particular by the primary piston 16 in a manner to be described in more detail later.
  • Each primary or secondary piston 18 is thus movable between a rear rest position, which is shown in FIGS. figures 1 a and 5a, and a position before applying a braking force, which is shown in FIGS. figures 3a and 7a , passing through intermediate positions that will be described later.
  • each primary or secondary piston 16 is resiliently biased towards its rear rest position against a stop which is formed in the body 14 and which will be described later.
  • the secondary piston 18 is biased backwards by a spring 20 which bears on a front end transverse face 22 of the bore 14 and on the secondary piston 18, and the primary piston 16 is resiliently biased towards the rear by a spring 24 which bears on a rear transverse face 61 of the secondary piston 18 and on the primary piston 16.
  • the spring 24 being in particular of great length, it is mounted around a sliding cylinder 23 which is interposed between the rear transverse face 61 of the secondary piston 18 and the primary piston 16.
  • the bore 14 comprises two primary sealing means 28 and rear 32 which are interposed respectively between the primary piston 16 and the bore 14 and two secondary means of sealing before 26 and rear 30 which are respectively interposed between the secondary piston 18 and the bore 14.
  • the primary sealing means before 28 delimits in the bore 14 a rear supply chamber 34 and a front pressure chamber 36.
  • the secondary means of sealing before 26 delimits in the bore 14 a rear feed chamber 38 and a front pressure chamber 40
  • the body 12 comprises a radial primary supply conduit 42 which connects a primary external reservoir (not shown) of hydraulic fluid to the feed chamber rear primary 34 and which opens between the two primary sealing means 28 and 32.
  • the radial primary conduit 42 is for example connected via an intermediate longitudinal conduit 44 to an orifice 46 which opens out of the body 14 and which is intended to receive an outlet mouth (not shown) of the associated primary reservoir.
  • the body 12 comprises a radial supply secondary duct 48 which connects a secondary external reservoir (not shown) of hydraulic fluid to the rear secondary supply chamber 38 and which opens out between the two secondary sealing means 26 and 30.
  • the body has two primary primary 50 and secondary 52 primary primary and secondary braking circuits that open into the associated primary 36 and secondary primary 40 front chambers.
  • the master cylinder 10 comprises means for communicating each primary 36 and secondary 36 primary front chamber with the primary rear 34 and secondary 38 associated secondary chamber. These communication means can be inhibited by the associated primary piston 16 and secondary 18 when it is moved axially forward towards its application position to isolate the primary pressure front chamber 36 or secondary 40 of the rear primary supply 34 or secondary 38 associated chamber, and thus allow the establishment of a braking pressure in the associated primary 36 or secondary 40 front pressure chamber.
  • each primary and secondary piston 16 comprises an associated front section 54, associated section 56 and a corresponding tubular rear segment 58, 60 with the same outside diameter "D", and includes a rear extent 62, 64 of the section before 54, 56 which slides in a bore 66, 68 of the rear section 58, 60.
  • Retaining means and elastic biasing means are interposed between a rear face 70, 72 of each front section 54, 56 and the bottom 74, 76 of the bore of the rear section 58, 60.
  • each rear section 58, 60 comprises for example a cylindrical guide surface 78, 80 which passes through the wall associated with the rear face of the associated front section and whose front end comprises a stop means 82, 84 to form the restraint means.
  • a spring 86, 88 is interposed between each rear face 70, 72 of each front section 54, 56 and the bottom 74, 76 of the bore of the rear section 58, 60.
  • each front section 54, 56 comprises at least one duct 90, 92, a first end of which opens into the associated pressure chamber 36, 40 and a second end of which opens into the periphery of the rear bearing surface 62, 64 between a rear shoulder face 94, 96 of the front section and a front face 98, 100 of the shoulder of the rear section 58, 60 to form a movable flap which , in the rest position of the piston 16, 18, opens into the supply chamber 36, 40 and allows communication between the front chambers 36, 40 and the rear chambers 34, 38.
  • the front face 98, 100 of the shoulder of each rear section 58, 60 comprises an annular seal 102, 104 made of elastomeric material that closes the valve sealingly.
  • each rear section 58, 60 therefore closes the associated valve and isolate the front chamber 36, 40 associated, which allows the rise in pressure of the hydraulic fluid.
  • each piston 16, 18 is monobloc and in particular tubular.
  • each piston 16, 18 comprises at least one conduit 106, 108, a first end of which opens into the front pressure chamber 36, 40 and a second end of which opens into the periphery of the piston 16, 18, of in order to communicate with the supply chamber 34, 38 in the rest position of the piston 16, 18 and so as to communicate with the front pressure chamber 36, 40 in the position of application of the piston.
  • the duct 106, 108 is arranged axially at the rear supply chamber 34, 38 and, in the advanced position of the piston 16, 18, which is shown more particularly to the figure 7a , the duct 106, 108 is arranged axially at the level of the front pressure chamber, that is to say on the other side of the front sealing means 28, 26 with respect to the rest position of the piston 16, 18, which therefore allows to isolate the chamber 36, 40 of associated front pressure and thus to allow the rise in pressure of the hydraulic fluid.
  • the front sealing means 28, 26 comprises a front seal 28, 26 which is mounted in a groove 110, 112 associated of the body 12.
  • An inner peripheral lip of the front seal 28, 26, arranged in contact with the piston 16, 18, is able to lift from the piston 16, 18 when it returns from its application position to its position resting to allow the hydraulic fluid, flowing between the bore 14 and the piston 16, 18 to re-feed the front pressure chamber 36, 40 from the radial conduit 42, 48 and supply tank.
  • FIGS. Figures 1b to 8b For example, the lip 114 of the seal 26 before sealing associated with the secondary piston 18 is shown in FIGS. Figures 1b to 8b .
  • each gasket 26, 28 may be previously wound on itself, substantially in the form of a "bean” and held in this configuration by means of a clamp (not shown) whose jaws 25 pinch the gasket 26 , 28.
  • the clamp is then introduced into the bore 14 of the body 10 until the seal 26, 28 has reached the groove 110, 112 and then its jaws 25 are maneuvered to release the seal 26, 28 which takes its place. shape and is positioned spontaneously in the groove 110, 112.
  • each gasket 26, 28 has a recess, which is arranged behind its lip and which is intended to receive a ring 27 of internal reinforcement.
  • This ring 27 of internal reinforcement is intended to prevent the extrusion of the seal 26, 28, as will be seen later.
  • Ring 27 is shown more particularly at figure 10 .
  • the ring is made of a substantially elastic material, and it comprises a frustoconical bearing surface 29 and an axial slot 31 arranged on its periphery 33 which are intended to facilitate its assembly, as will be seen later with reference to Figures 12 to 14 .
  • the ring may comprise axial grooves 35 arranged on the inner face 37 of its periphery 33.
  • the ring 27 is made of an elastomeric material.
  • the lip of the front seal 26 is in contact with the periphery of the piston 18, and the lip of the front seal 28 is in contact with the periphery of the piston 16.
  • the rear supply chambers 34, 38 being in communication with the front chambers 36, 40, the seal is subjected to equal pressure on each of its faces.
  • the figures 1b and 5b illustrate in particular the detail of the lip 114 of the front seal 26 which is in contact with the piston 18.
  • an inner rear face 118 of the seal 26 is disjoined from the ring 27, which allows the circulation of the hydraulic fluid.
  • the Figures 2a and 6a represent a position of inhibition of the communication means.
  • the advance of the primary piston 16 has caused the closure of the conduit 90 associated with the piston 16 by pressing the annular seal 102 against the rear face 94 of the shoulder of the front section 54 of the piston 16.
  • the figure 6b illustrates the action of the pressure forces, represented by arrows, on the front face 116 of the lip 114 of the seal 26. These pressure forces press the lip 116 of the seal 26 against the piston 18 and press the inner rear face 118 of the seal 26 against the ring 27, thus ensuring a good seal.
  • the figures 3a and 7a represent a position of application of a braking force by the pistons 16 and 18.
  • the advance of the primary pistons 16 and 18 caused the closure of the conduits 90, 92 associated with the first embodiment and the conduits 106 associated with the second embodiment.
  • Each of these ducts has advanced in a position relative to the respective front seal 26, 28 which is opposite to that which it previously occupied in the rest position.
  • the hydraulic brake fluid is under pressure in the two front chambers 36 and 40.
  • the front faces of the seals 28 and 26 are subjected to a pressure which plates against the periphery of the respective pistons 16 and 18.
  • the arrows of the figure 3b illustrate the action of the pressure forces on the front face 116 of the lip 114 of the seal 26 associated with the first embodiment.
  • the figure 7b illustrates the action of the pressure forces, represented by arrows, on the front face 116 of the lip 114 of the seal 26 associated with the second embodiment.
  • FIGS 4a and 8a represent a restoring position of the front chambers 36, 40 by the radial conduits 42, 48 and the associated tanks (not shown) when the driver releases his force on the end 19 of the primary piston 16.
  • the vacuum forces take off the lip 116 of the piston 18 and take off the inner rear face 118 of the seal 26 of the ring 27, which more particularly allows the hydraulic fluid to flow from the duct 48 to the front secondary pressure chamber 40 in flowing between the rear face 118 of the gasket 26 and the ring 27.
  • the body 12 preferably comprises a pair of annular bearing surfaces 120, 122 which are arranged on either side of the front seal 26 associated with the piston 18, and a front pair of annular bearings 124, 126 which are arranged on either side of the front seal 28 associated with the piston 16.
  • bearing surfaces 120, 122, 124, 126 allow the guiding of the pistons 16, 18 in the bore 14.
  • Each of these annular bearing surfaces 120, 122, 124, 126 comprises at least one groove 128 for circulating the hydraulic fluid. This configuration makes it possible to provide precise guidance of the piston 16, 18 while allowing the supply of the radial duct 42, 48 with a satisfactory flow rate.
  • the ring 27 advantageously avoids the extrusion of the front seal 28 in the at least one groove 128.
  • annular bearing surfaces 120, 122 comprise a plurality of helical grooves 124.
  • the rear sealing means 30, 32 consists of a rear seal 30, 32 which is mounted in a groove 130, 132 of the body 12 and of which an inner peripheral lip is arranged in contact with the piston 16, 18 associated.
  • the body comprises a rear pair of annular bearing surfaces 134, 136 which are arranged on either side of the rear seal 30 associated with the piston 18 and a rear pair of annular bearing surfaces 138, 140 which are arranged on both sides. other of the rear seal 32 associated with the piston 16.
  • These bearing surfaces 134, 136, 138, 140 allow the guide of the pistons 16, 18 associated in the bore 14.
  • the stop means of the pistons 16, 18 comprise at the end of each piston an external elastic ring 142, 144 which is capable, in the rest position of the piston 16, 18, of come into contact with a shoulder face before the annular bearing surface 124, 120 which is part of the front pair of annular bearings.
  • FIGS. 12 to 14 illustrate three successive steps of assembly in the body 12 of the reinforcement ring 27 associated with the seal 26 of the second embodiment.
  • the tool 150 is tubular and has a front section 152 which is substantially the diameter of the bore 14, and a rear section 154 which is substantially of a diameter equal to the inner diameter of the compressed reinforcement ring 27.
  • the tool 150 comprises a frustoconical chamfer 156 at the rear end of its front section 152.
  • the length of the front section 152 is provided so that the rear end of the front section 152 coincides axially substantially with the groove 112.
  • the tool 160 is substantially tubular and has a front section 162 which is substantially the average diameter of the compressed reinforcement ring 27.
  • the tool 160 has a frustoconical chamfer 166 at the front end of its front section 162. It also comprises a rear section 164 forming a prehensid wheel, with a larger diameter than the front section 162.
  • the tool 170 is substantially tubular and has a front section 172 which is substantially of an inner diameter equal to the outer diameter of the compressed reinforcement ring 27. It also comprises a rear section 174 forming a grip wheel, with a larger diameter than the front section 172.
  • the ring 27 is compressed and then threaded onto the rear section 154 of the tool 150. Then the tool 160 is threaded in an intermediate axial position in the tool 170 and the tool 150.
  • the set of three tools 150 160, 170 and the ring 27 is introduced into the bore 14 of the body 12.
  • the ring 27 is then held axially by the end of the front section 162 of the tool 160, and is held radially by the front section 172 of the tool 170, with an axial clearance J between the ring 27 and the front section 152 of the tool 150, as shown in FIG. figure 12 .
  • the tool 160 is pushed forward so as to reduce the clearance J.
  • the ring 27 escapes from the front section 172 and spontaneously resumes its shape bearing on the frustoconical chamfer 166 of the tool 160.
  • the invention therefore makes it possible to have a master cylinder provided with a seal of high reliability.

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  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Of Braking Force In Braking Systems (AREA)
  • Fluid-Damping Devices (AREA)
  • Walking Sticks, Umbrellas, And Fans (AREA)

Abstract

A master cylinder (10) having an axial body (12) with a bore (14) for receving a piston (16, 18), a front seal (26, 28) and a rear seal (30, 32) to delimit a rear supply chamber (34, 38) from a front pressure chamber (36, 40). A supply duct (42, 48) in the body (12) that connects a reservoir to the rear supply chamber (34, 38) has an opening between the front seal (26, 28) and the rear seal (26, 28). The front seal (26, 28) is mounted in a groove (110, 112) of the body (12) and has an interior lip that contacts the piston (16, 18) and lifts off the piston (16, 18) as the piston (16, 18) returns from a position of application to a position of rest to allow hydraulic fluid to be resupply the front pressure chamber (36, 40).

Description

L'invention concerne un maître-cylindre de freinage pour un véhicule automobile.The invention relates to a brake master cylinder for a motor vehicle.

L'invention concerne plus particulièrement un maître-cylindre de freinage pour un véhicule automobile, du type qui comporte un corps sensiblement axial à l'intérieur d'un alésage duquel est monté coulissant au moins un piston axial, qui est susceptible d'être actionné par un conducteur du véhicule entre une position arrière de repos et une position avant d'application d'un effort de freinage, et qui est rappelé élastiquement vers sa position arrière de repos à l'encontre d'une butée formée dans le corps, du type dans lequel l'alésage comporte deux moyens d'étanchéité avant et arrière qui sont interposés entre le piston et l'alésage, le moyen d'étanchéité avant délimitant dans l'alésage une chambre d'alimentation arrière et une chambre de pression avant, du type dans lequel le corps comporte un conduit radial d'alimentation qui relie un réservoir extérieur de fluide hydraulique à la chambre d'alimentation arrière et qui débouche entre les deux moyens d'étanchéité, du type dans lequel le corps comporte un perçage d'alimentation d'un circuit de freinage qui débouche dans la chambre de pression avant, du type qui comporte des moyens de mise en communication de la chambre de pression avant et de la chambre d'alimentation arrière qui sont susceptibles d'être inhibés par le piston lorsqu'il est mû axialement vers l'avant vers sa position d'application pour isoler la chambre de pression avant de la chambre d'alimentation arrière et permettre ainsi l'établissement d'une pression de freinage dans la chambre de pression avant.The invention relates more particularly to a brake master cylinder for a motor vehicle, of the type which comprises a substantially axial body within a bore of which is slidably mounted at least one axial piston, which can be actuated by a driver of the vehicle between a rear position of rest and a position before application of a braking force, and which is resiliently biased towards its rear rest position against a stop formed in the body, the a type in which the bore has two front and rear sealing means which are interposed between the piston and the bore, the front sealing means defining in the bore a rear supply chamber and a front pressure chamber, of the type in which the body comprises a radial supply duct which connects an external reservoir of hydraulic fluid to the rear supply chamber and which opens out between the two means of supply. sealing, of the type in which the body comprises a feed hole of a braking circuit which opens into the front pressure chamber, of the type which comprises means for communicating the front pressure chamber and the chamber which are likely to be inhibited by the piston when it is moved axially forward towards its application position to isolate the front pressure chamber of the rear feed chamber and thus allow the establishment a braking pressure in the front pressure chamber.

On connaît de nombreux exemples de maîtres-cylindre de freinage de ce type. Voir par exemple US 4945728 , EP0 115223 , DE 19652486 ou EP0 159236 .Many examples of braking master cylinders of this type are known. See for example US 4945728 , EP0 115223 , From 19652486 or EP0 159236 .

Dans la plupart des maîtres cylindres de ce type, au moins un des deux moyens d'étanchéité est porté par le piston. Il est donc sujet à une usure importante du fait des mouvements de va-et-vient qu'effectue le piston dans l'alésage du corps du servomoteur au cours des freinages successifs.In most master cylinders of this type, at least one of the two sealing means is carried by the piston. It is therefore subject to significant wear due to the reciprocating movements of the piston in the bore of the servomotor body during successive braking.

Cette usure est susceptible de compromettre l'étanchéité des chambres d'alimentation et de pression du servomoteur, ce qui peut avoir des conséquences d'autant plus graves que la plupart des maîtres cylindres actuels sont conçus pour présenter des sections de piston importantes afin de permettre l'établissement d'une pression de freinage élevée.This wear is likely to compromise the tightness of the supply and pressure chambers of the servomotor, which can have consequences all the more serious as most current master cylinders are designed to have large piston sections to allow establishing a high braking pressure.

Pour remédier à cet inconvénient, l'invention propose un maître-cylindre de freinage du type décrit précédemment, qui comporte au moins un joint d'étanchéité porté par l'alésage du corps.To overcome this drawback, the invention provides a brake master cylinder of the type described above, which comprises at least one seal carried by the bore of the body.

Dans ce but, l'invention propose un maître-cylindre de freinage du type décrit précédemment, caractérisé en ce que le moyen d'étanchéité avant comporte un joint d'étanchéité avant qui est monté dans une gorge du corps et dont une lèvre périphérique intérieure, agencée au contact du piston, est susceptible de se soulever du piston lorsqu'il revient de sa position d'application vers sa position de repos pour permettre au fluide hydraulique, en circulant entre l'alésage et le piston de ré-alimenter la chambre de pression avant à partir du conduit radial d'alimentation et du réservoir.

  • le corps comporte une paire avant de portées annulaires qui sont agencées de part et d'autre du joint d'étanchéité avant pour permettre le guidage du piston dans l'alésage et qui comportent au moins une rainure de circulation du fluide hydraulique,
  • les portées annulaires de la paire avant comportent une pluralité de rainures hélicoïdales,
For this purpose, the invention proposes a braking master cylinder of the type described above, characterized in that the front sealing means comprises a front seal which is mounted in a groove of the body and of which an inner peripheral lip , arranged in contact with the piston, is able to lift the piston when it returns from its application position to its rest position to allow the hydraulic fluid, circulating between the bore and the piston to re-feed the chamber front pressure from the radial supply duct and the tank.
  • the body comprises a pair of annular bearing surfaces which are arranged on either side of the front seal to allow the guide of the piston in the bore and which comprise at least one groove for the circulation of the hydraulic fluid,
  • the annular bearing surfaces of the front pair comprise a plurality of helical grooves,

Selon d'autres caractéristiques de l'invention:

  • le piston est monobloc, notamment tubulaire, et comporte au moins un conduit dont une première extrémité débouche dans la chambre de pression avant et dont une seconde extrémité débouche dans la périphérie du piston, de manière communiquer avec la chambre d'alimentation en position de repos du piston pour former les moyens de communication, et de manière à communiquer avec la chambre de pression avant en position d'application du piston pour inhiber les moyens de communication,
  • le joint comporte un anneau de renfort intérieur qui est destiné à éviter l'extrusion du joint au passage de la seconde extrémité du conduit du piston,
  • l'anneau est réalisé en un matériau sensiblement élastique, et il comporte une portée tronconique et une fente axiale agencée sur sa périphérie qui sont destinées à faciliter son montage,
  • l'anneau comporte au moins une fente axiale agencée sur la face intérieure de sa périphérie,
  • l'anneau est réalisé en un matériau élastomère,
  • le piston comporte un tronçon avant et un tronçon arrière tubulaires de même diamètre extérieur, une portée arrière du tronçon avant coulissant dans un alésage du tronçon arrière, et des moyens de retenue et des moyens de sollicitation élastique sont interposés entre une face arrière du tronçon avant et le fond de l'alésage du tronçon arrière,
  • le tronçon avant comporte au moins un conduit dont une première extrémité débouche dans la chambre de pression avant et dont une seconde extrémité débouche dans la périphérie de la portée arrière entre une face arrière d'épaulement du tronçon avant et une face avant d'épaulement du tronçon arrière pour former un clapet mobile qui, en position de repos du piston, débouche dans la chambre d'alimentation et constitue les moyens de communication,
  • la face avant d'épaulement du tronçon arrière comporte un joint annulaire,
  • le moyen d'étanchéité arrière est constitué d'un joint d'étanchéité arrière qui est monté dans une gorge du corps et dont une lèvre périphérique intérieure est agencée au contact du piston,
  • le corps comporte une paire arrière de portées annulaires qui sont agencées de part et d'autre du joint d'étanchéité arrière pour permettre le guidage du piston dans l'alésage,
  • le piston comporte à son extrémité un anneau élastique extérieur qui est susceptible, dans la position de repos du piston, de venir au contact d'une face d'épaulement avant de la portée annulaire avant de la paire avant de portées annulaires formant butée,
  • le piston est rappelé élastiquement vers sa position arrière de repos par un ressort,
  • le maître-cylindre est un maître-cylindre de type "tandem" qui comporte, d'arrière en avant, deux pistons primaire et secondaire qui délimitent dans l'alésage du corps des chambres d'alimentation primaire et secondaire et des chambres de pression primaire et secondaire, le piston primaire étant rappelé élastiquement vers sa position arrière de repos par l'intermédiaire d'un ressort prenant appui entre une face arrière du piston secondaire et une face avant du piston primaire.
According to other features of the invention:
  • the piston is integral, in particular tubular, and comprises at least one duct, a first end of which opens into the front pressure chamber and a second end of which opens into the periphery of the piston, so as to communicate with the supply chamber in the rest position of the piston to form the communication means, and to communicate with the front pressure chamber in the position of application of the piston to inhibit the communication means,
  • the seal comprises an inner reinforcing ring which is intended to prevent the extrusion of the seal at the passage of the second end of the piston duct,
  • the ring is made of a substantially elastic material, and it comprises a frustoconical bearing surface and an axial slot arranged on its periphery which are intended to facilitate its assembly,
  • the ring comprises at least one axial slot arranged on the inner face of its periphery,
  • the ring is made of an elastomeric material,
  • the piston comprises a front section and a tubular rear section with the same outside diameter, a rear section of the front section sliding in a bore of the rear section, and retaining means and elastic biasing means are interposed between a rear face of the front section. and the bottom of the bore of the rear section,
  • the front section comprises at least one duct, a first end of which opens into the front pressure chamber and a second end of which opens into the periphery of the rear seat between a rear shoulder face of the front section and a front shoulder face of the rear section to form a movable valve which, in the rest position of the piston, opens into the feed chamber and constitutes the means of communication,
  • the shoulder front face of the rear section comprises an annular seal,
  • the rear sealing means is constituted by a rear seal which is mounted in a groove of the body and of which an inner peripheral lip is arranged in contact with the piston,
  • the body comprises a rear pair of annular bearing surfaces which are arranged on either side of the rear seal to enable the piston to be guided in the bore,
  • the piston comprises at its end an outer elastic ring which is capable, in the rest position of the piston, of coming into contact with a shoulder face before the front annular bearing surface of the pair before annular abutment abutments,
  • the piston is resiliently returned to its rear rest position by a spring,
  • the master cylinder is a "tandem" type master cylinder which comprises, from rear to front, two primary and secondary pistons which delimit in the bore of the body primary and secondary supply chambers and primary pressure chambers and secondary, the primary piston being resiliently returned to its rear rest position by means of a spring bearing between a rear face of the secondary piston and a front face of the primary piston.

D'autres caractéristiques et avantages de l'invention apparaîtront à la lecture de la description détaillée qui suit pour la compréhension de laquelle on se reportera aux dessins annexés dans lesquels :

  • la figure 1a est une vue en coupe axiale d'un premier mode de réalisation d'un maître-cylindre de type "tandem" selon l'invention représenté en position de repos ;
  • la figure 2a est une vue du maître-cylindre de la figure 1a représenté en position d'inhibition des deux moyens de mise en communication ;
  • la figure 3a est une vue du maître-cylindre de la figure 1 a représenté en position d'application d'un effort de freinage ;
  • la figure 4a est une vue du maître-cylindre de la figure 1 a représenté en position de réalimentation des conduits radiaux d'alimentation et des réservoirs ;
  • la figure 5a est une vue en coupe axiale d'un second mode de réalisation d'un maître-cylindre de type "tandem" selon l'invention représenté en position de repos ;
  • la figure 6a est une vue du maître-cylindre de la figure 5a représenté en position d'inhibition des deux moyens de mise en communication ;
  • la figure 7a est une vue du maître-cylindre de la figure 5a représenté en position d'application d'un effort de freinage ;
  • la figure 8a est une vue du maître-cylindre de la figure 5a représenté en position de réalimentation des conduits radiaux d'alimentation et des réservoirs ;
  • les figure 1b à 8b sont des vues de détail du joint d'étanchéité avant associé au piston secondaire selon les figures 1a à 8a ;
  • la figure 9a est une demi-vue en perspective du corps du maître-cylindre ;
  • la figure 9b est une vue de détail des rainures hélicoïdales du corps de la figure 1 ;
  • la figure 10 est une vue en perspective de l'anneau de renfort ;
  • la figure 11 est une vue, en bout d'un joint d'étanchéité et de son outil de montage représentés avant le montage du joint; et
  • les figure 12 à 14 sont des vues en coupe axiale illustrant trois étapes successives du montage d'un anneau de renfort du joint d'étanchéité de la figure 2a à l'intérieur de l'alésage du maître-cylindre.
Other features and advantages of the invention will appear on reading the detailed description which follows for the understanding of which reference will be made to the appended drawings in which:
  • the figure 1a is an axial sectional view of a first embodiment of a master cylinder "tandem" type according to the invention shown in the rest position;
  • the figure 2a is a view of the master cylinder of the figure 1a shown in the inhibiting position of the two communication means;
  • the figure 3a is a view of the master cylinder of the figure 1 represented in the application position of a braking force;
  • the figure 4a is a view of the master cylinder of the figure 1 has represented in the feed position of the radial supply ducts and tanks;
  • the figure 5a is an axial sectional view of a second embodiment of a master cylinder "tandem" type according to the invention shown in the rest position;
  • the figure 6a is a view of the master cylinder of the figure 5a shown in the inhibiting position of the two communication means;
  • the figure 7a is a view of the master cylinder of the figure 5a shown in the application position of a braking force;
  • the figure 8a is a view of the master cylinder of the figure 5a shown in the feed position of the radial supply ducts and tanks;
  • the figure 1b to 8b are detailed views of the front seal associated with the secondary piston according to the Figures 1a to 8a ;
  • the figure 9a is a half-perspective view of the body of the master cylinder;
  • the figure 9b is a detail view of the helical grooves of the body of the figure 1 ;
  • the figure 10 is a perspective view of the reinforcement ring;
  • the figure 11 is a view, at the end of a seal and its mounting tool shown before mounting the seal; and
  • the figure 12 to 14 are views in axial section illustrating three successive stages of mounting a reinforcement ring of the seal of the figure 2a inside the bore of the master cylinder.

Dans la description qui va suivre, des chiffres de référence identiques désignent des pièces identiques ou ayant des fonctions similaires.In the following description, like reference numerals designate like parts or having similar functions.

Par convention, les termes "avant" et "arrière", désignent respectivement des éléments ou des positions orientés respectivement vers la gauche et la droite des figures.By convention, the terms "front" and "rear" respectively designate elements or positions respectively oriented to the left and right of the figures.

On a représenté sur les figures 1a à 8a l'ensemble d'un maître-cylindre 10 de freinage pour un véhicule automobile.We have shown on Figures 1a to 8a the assembly of a brake master cylinder 10 for a motor vehicle.

De manière connue, dans les modes de réalisation préférés de l'invention, le maître-cylindre 10 est un maître-cylindre de type "tandem" qui comporte un corps 12 sensiblement axial d'axe A à l'intérieur d'un alésage 14 duquel sont montés coulissants deux pistons axiaux 16 et 18.In known manner, in the preferred embodiments of the invention, the master cylinder 10 is a "tandem" type master cylinder which comprises a substantially axial body 12 of axis A inside a bore 14 of which are slidably mounted two axial pistons 16 and 18.

Cette configuration n'est toutefois pas limitative de l'invention et le maître-cylindre 10 pourrait être un maître-cylindre simple ne comportant qu'un seul piston coulissant.This configuration is however not limited to the invention and the master cylinder 10 could be a simple master cylinder having only one sliding piston.

Le piston 16, dit piston primaire 16, est destiné à permettre l'établissement d'une pression hydraulique dans un circuit primaire de freinage du véhicule (non représenté), et le piston 18, dit piston secondaire 18, est destiné à permettre l'établissement d'une pression hydraulique dans un circuit secondaire de freinage du véhicule (non représenté) qui est indépendant du circuit primaire de freinage du véhicule.The piston 16, said primary piston 16, is intended to allow the establishment of a hydraulic pressure in a primary braking circuit of the vehicle (not shown), and the piston 18, said secondary piston 18, is intended to allow the establishing a hydraulic pressure in a secondary braking circuit of the vehicle (not shown) which is independent of the primary brake circuit of the vehicle.

Le piston primaire 16 est susceptible d'être actionné directement par un conducteur du véhicule. Par exemple, une extrémité arrière 19 du piston primaire 16 est susceptible d'être reliée à un servomoteur (non représenté) qui amplifie les efforts exercés sur une pédale de freinage du véhicule.The primary piston 16 can be actuated directly by a driver of the vehicle. For example, a rear end 19 of the primary piston 16 may be connected to a servomotor (not shown) which amplifies the forces exerted on a brake pedal of the vehicle.

Le piston secondaire 18 est susceptible d'être actionné indirectement par le conducteur du véhicule, notamment par le piston primaire 16 d'une façon qui sera décrite plus en détail ultérieurement.The secondary piston 18 may be actuated indirectly by the driver of the vehicle, in particular by the primary piston 16 in a manner to be described in more detail later.

Chaque piston primaire 16 ou secondaire 18 est ainsi mobile entre une position arrière de repos, qui est représentée aux figures 1 a et 5a, et une position avant d'application d'un effort de freinage, qui est représentée aux figures 3a et 7a, en passant par des positions intermédiaires qui seront décrites ultérieurement.Each primary or secondary piston 18 is thus movable between a rear rest position, which is shown in FIGS. figures 1 a and 5a, and a position before applying a braking force, which is shown in FIGS. figures 3a and 7a , passing through intermediate positions that will be described later.

De manière connue, chaque piston primaire 16 ou secondaire 18 est rappelé élastiquement vers sa position arrière de repos à l'encontre d'une butée qui est formée dans le corps 14 et qui sera décrite ultérieurement.In known manner, each primary or secondary piston 16 is resiliently biased towards its rear rest position against a stop which is formed in the body 14 and which will be described later.

En particulier, le piston secondaire 18 est rappelé vers l'arrière par un ressort 20 qui prend appui sur une face 22 transversale d'extrémité avant de l'alésage 14 et sur le piston secondaire 18, et le piston primaire 16 est rappelé élastiquement vers l'arrière par un ressort 24 qui prend appui sur une face 61 transversale arrière du piston secondaire 18 et sur le piston primaire 16. Plus particulièrement, le ressort 24 étant notamment de grande longueur, il est monté autour d'un vérin coulissant 23 qui est interposé entre la face 61 transversale arrière du piston secondaire 18 et le piston primaire 16.In particular, the secondary piston 18 is biased backwards by a spring 20 which bears on a front end transverse face 22 of the bore 14 and on the secondary piston 18, and the primary piston 16 is resiliently biased towards the rear by a spring 24 which bears on a rear transverse face 61 of the secondary piston 18 and on the primary piston 16. More particularly, the spring 24 being in particular of great length, it is mounted around a sliding cylinder 23 which is interposed between the rear transverse face 61 of the secondary piston 18 and the primary piston 16.

L'alésage 14 comporte deux moyens primaires d'étanchéité avant 28 et arrière 32 qui sont interposés respectivement entre le piston primaire 16 et l'alésage 14 et deux moyens secondaires d'étanchéité avant 26 et arrière 30 qui sont interposés respectivement entre le piston secondaire 18 et l'alésage 14.The bore 14 comprises two primary sealing means 28 and rear 32 which are interposed respectively between the primary piston 16 and the bore 14 and two secondary means of sealing before 26 and rear 30 which are respectively interposed between the secondary piston 18 and the bore 14.

De ce fait, le moyen primaire d'étanchéité avant 28 délimite dans l'alésage 14 une chambre 34 d'alimentation arrière et une chambre 36 de pression avant. De même, le moyen secondaire d'étanchéité avant 26 délimite dans l'alésage 14 une chambre 38 d'alimentation arrière et une chambre 40 de pression avantTherefore, the primary sealing means before 28 delimits in the bore 14 a rear supply chamber 34 and a front pressure chamber 36. Similarly, the secondary means of sealing before 26 delimits in the bore 14 a rear feed chamber 38 and a front pressure chamber 40

Le corps 12 comporte un conduit 42 primaire radial d'alimentation qui relie un réservoir extérieur primaire (non représenté) de fluide hydraulique à la chambre d'alimentation primaire arrière 34 et qui débouche entre les deux moyens primaires d'étanchéité 28 et 32.The body 12 comprises a radial primary supply conduit 42 which connects a primary external reservoir (not shown) of hydraulic fluid to the feed chamber rear primary 34 and which opens between the two primary sealing means 28 and 32.

En particulier, le conduit 42 primaire radial est par exemple relié par l'intermédiaire d'un conduit longitudinal intermédiaire 44 à un orifice 46 qui débouche à l'extérieur du corps 14 et qui est destiné à recevoir une bouche de sortie (non représentée) du réservoir primaire associé.In particular, the radial primary conduit 42 is for example connected via an intermediate longitudinal conduit 44 to an orifice 46 which opens out of the body 14 and which is intended to receive an outlet mouth (not shown) of the associated primary reservoir.

Le corps 12 comporte un conduit 48 secondaire radial d'alimentation qui relie un réservoir extérieur secondaire (non représenté) de fluide hydraulique à la chambre d'alimentation secondaire arrière 38 et qui débouche entre les deux moyens secondaires d'étanchéité 26 et 30.The body 12 comprises a radial supply secondary duct 48 which connects a secondary external reservoir (not shown) of hydraulic fluid to the rear secondary supply chamber 38 and which opens out between the two secondary sealing means 26 and 30.

Le corps comporte deux perçages primaire 50 et secondaire 52 d'alimentation des circuits de freinage primaire et secondaires associés qui débouchent dans les chambres avant de pression primaire 36 et secondaire 40 associées.The body has two primary primary 50 and secondary 52 primary primary and secondary braking circuits that open into the associated primary 36 and secondary primary 40 front chambers.

De manière connue, le maître-cylindre 10 comporte des moyens de mise en communication de chaque chambre avant de pression primaire 36 et secondaire 40 avec la chambre arrière d'alimentation primaire 34 et secondaire 38 associée. Ces moyens de mise en communication sont susceptibles d'être inhibés par le piston primaire 16 et secondaire 18 associé lorsqu'il est mû axialement vers l'avant vers sa position d'application pour isoler la chambre avant de pression primaire 36 ou secondaire 40 de la chambre arrière d'alimentation primaire 34 ou secondaire 38 associée, et permettre ainsi l'établissement d'une pression de freinage dans la chambre avant de pression primaire 36 ou secondaire 40 associée.In known manner, the master cylinder 10 comprises means for communicating each primary 36 and secondary 36 primary front chamber with the primary rear 34 and secondary 38 associated secondary chamber. These communication means can be inhibited by the associated primary piston 16 and secondary 18 when it is moved axially forward towards its application position to isolate the primary pressure front chamber 36 or secondary 40 of the rear primary supply 34 or secondary 38 associated chamber, and thus allow the establishment of a braking pressure in the associated primary 36 or secondary 40 front pressure chamber.

Selon un premier mode de réalisation de l'invention qui est décrit aux figures 1a à 4a et 1b à 4b, chaque piston primaire 16 et secondaire 18 comporte un tronçon avant 54, 56 associé et un tronçon arrière 58, 60 associé, tubulaires, de même diamètre extérieur "D", et il comporte une portée arrière 62, 64 du tronçon avant 54, 56 qui coulisse dans un alésage 66, 68 du tronçon arrière 58, 60.According to a first embodiment of the invention which is described in Figures 1a to 4a and 1b to 4b each primary and secondary piston 16 comprises an associated front section 54, associated section 56 and a corresponding tubular rear segment 58, 60 with the same outside diameter "D", and includes a rear extent 62, 64 of the section before 54, 56 which slides in a bore 66, 68 of the rear section 58, 60.

Des moyens de retenue et des moyens de sollicitation élastique sont interposés entre une face arrière 70, 72 de chaque tronçon avant 54, 56 et le fond 74, 76 de l'alésage du tronçon arrière 58, 60.Retaining means and elastic biasing means are interposed between a rear face 70, 72 of each front section 54, 56 and the bottom 74, 76 of the bore of the rear section 58, 60.

En particulier, chaque tronçon arrière 58, 60 comporte par exemple une portée 78, 80 cylindrique de guidage qui traverse la paroi associée à la face arrière du tronçon avant associé et dont une extrémité avant comporte un moyen d'arrêt 82, 84 pour former les moyens de retenue.In particular, each rear section 58, 60 comprises for example a cylindrical guide surface 78, 80 which passes through the wall associated with the rear face of the associated front section and whose front end comprises a stop means 82, 84 to form the restraint means.

D'autre part un ressort 86, 88 est interposé entre chaque face arrière 70, 72 de chaque tronçon avant 54, 56 et le fond 74, 76 de l'alésage du tronçon arrière 58, 60.On the other hand a spring 86, 88 is interposed between each rear face 70, 72 of each front section 54, 56 and the bottom 74, 76 of the bore of the rear section 58, 60.

Comment l'illustrent les figures 1a à 4a, et plus particulièrement les figures 1b à 4b, pour former les moyens de mise en communication des chambres de pression avant et d'alimentation arrière, chaque tronçon avant 54, 56 comporte au moins un conduit 90, 92 dont une première extrémité débouche dans la chambre de pression 36, 40 avant associée et dont une seconde extrémité débouche dans la périphérie de la portée arrière 62, 64 entre une face arrière d'épaulement 94, 96 du tronçon avant et une face avant 98, 100 d'épaulement du tronçon arrière 58, 60 pour former un clapet mobile qui, en position de repos du piston 16, 18, débouche dans la chambre d'alimentation 36, 40 et permet la communication entre les chambres avant 36, 40 et les chambres arrière 34, 38.How does it illustrate Figures 1a to 4a , and more particularly Figures 1b to 4b , to form the communication means of the front pressure and rear supply chambers, each front section 54, 56 comprises at least one duct 90, 92, a first end of which opens into the associated pressure chamber 36, 40 and a second end of which opens into the periphery of the rear bearing surface 62, 64 between a rear shoulder face 94, 96 of the front section and a front face 98, 100 of the shoulder of the rear section 58, 60 to form a movable flap which , in the rest position of the piston 16, 18, opens into the supply chamber 36, 40 and allows communication between the front chambers 36, 40 and the rear chambers 34, 38.

Avantageusement, la face avant 98, 100 d'épaulement de chaque tronçon arrière 58, 60 comporte un joint annulaire 102, 104 en matériau élastomère qui permet de fermer ce clapet de manière étanche.Advantageously, the front face 98, 100 of the shoulder of each rear section 58, 60 comprises an annular seal 102, 104 made of elastomeric material that closes the valve sealingly.

L'avancée de chaque tronçon arrière 58, 60 permet donc de fermer le clapet associé et d'isoler la chambre avant 36, 40 associée, ce qui permet la montée en pression du fluide hydraulique.The advance of each rear section 58, 60 therefore closes the associated valve and isolate the front chamber 36, 40 associated, which allows the rise in pressure of the hydraulic fluid.

Selon un second mode de réalisation de l'invention qui est décrit aux figures 5a à 8a et 5b à 8b, chaque piston 16, 18 est monobloc et notamment tubulaire. Pour former les moyens de communication, chaque piston 16, 18 comporte au moins un conduit 106, 108 dont une première extrémité débouche dans la chambre de pression avant 36, 40 et dont une seconde extrémité débouche dans la périphérie du piston 16, 18, de manière à communiquer avec la chambre d'alimentation 34, 38 en position de repos du piston 16, 18 et de manière à communiquer avec la chambre de pression avant 36, 40 en position d'application du piston. De la sorte, en position de repos de chaque piston 16, 18, le conduit 106, 108 est agencé axialement au niveau de la chambre d'alimentation arrière 34, 38 et, dans la position avancée du piston 16, 18, qui est représentée plus particulièrement à la figure 7a, le conduit 106, 108 est agencé axialement au niveau de la chambre de pression avant, c'est à dire de l'autre côté du moyen d'étanchéité avant 28, 26 par rapport à la position de repos du piston 16, 18, ce qui permet par conséquent d'isoler la chambre 36, 40 de pression avant associée et ainsi de permettre la montée en pression du fluide hydraulique.According to a second embodiment of the invention which is described in FIGS. 5a to 8a and 5b to 8b each piston 16, 18 is monobloc and in particular tubular. To form the communication means, each piston 16, 18 comprises at least one conduit 106, 108, a first end of which opens into the front pressure chamber 36, 40 and a second end of which opens into the periphery of the piston 16, 18, of in order to communicate with the supply chamber 34, 38 in the rest position of the piston 16, 18 and so as to communicate with the front pressure chamber 36, 40 in the position of application of the piston. In this way, in the rest position of each piston 16, 18, the duct 106, 108 is arranged axially at the rear supply chamber 34, 38 and, in the advanced position of the piston 16, 18, which is shown more particularly to the figure 7a , the duct 106, 108 is arranged axially at the level of the front pressure chamber, that is to say on the other side of the front sealing means 28, 26 with respect to the rest position of the piston 16, 18, which therefore allows to isolate the chamber 36, 40 of associated front pressure and thus to allow the rise in pressure of the hydraulic fluid.

Conformément à l'invention, et quel que soit le mode de réalisation choisi de l'invention, le moyen d'étanchéité avant 28, 26 est comporte un joint d'étanchéité avant 28, 26 qui est monté dans une gorge 110, 112 associée du corps 12. Une lèvre périphérique intérieure du joint d'étanchéité avant 28, 26, agencée au contact du piston 16, 18, est susceptible de se soulever du piston 16, 18 lorsqu'il revient de sa position d'application vers sa position de repos pour permettre au fluide hydraulique, en circulant entre l'alésage 14 et le piston 16, 18 de ré-alimenter la chambre de pression avant 36, 40 à partir du conduit radial 42, 48 d'alimentation et du réservoir.According to the invention, and whatever the chosen embodiment of the invention, the front sealing means 28, 26 comprises a front seal 28, 26 which is mounted in a groove 110, 112 associated of the body 12. An inner peripheral lip of the front seal 28, 26, arranged in contact with the piston 16, 18, is able to lift from the piston 16, 18 when it returns from its application position to its position resting to allow the hydraulic fluid, flowing between the bore 14 and the piston 16, 18 to re-feed the front pressure chamber 36, 40 from the radial conduit 42, 48 and supply tank.

A titre d'exemple, la lèvre 114 du joint 26 avant d'étanchéité associé au piston secondaire 18 est représentée aux figures 1b à 8b.For example, the lip 114 of the seal 26 before sealing associated with the secondary piston 18 is shown in FIGS. Figures 1b to 8b .

Comme l'illustre la figure 11, chaque joint 26, 28 peut être préalablement enroulé sur lui-même, sensiblement selon la forme d'un "haricot" et maintenu dans cette configuration à l'aide d'une pince (non représentée) dont les mors 25 pincent le joint 26, 28.As illustrated by figure 11 each gasket 26, 28 may be previously wound on itself, substantially in the form of a "bean" and held in this configuration by means of a clamp (not shown) whose jaws 25 pinch the gasket 26 , 28.

La pince est ensuite introduite dans l'alésage 14 du corps 10 jusqu'à ce que le joint 26, 28 soit parvenu axialement au niveau de la gorge 110, 112 puis ses mors 25 sont manoeuvrés pour relâcher le joint 26, 28 qui reprend sa forme et se positionne spontanément dans la gorge 110, 112.The clamp is then introduced into the bore 14 of the body 10 until the seal 26, 28 has reached the groove 110, 112 and then its jaws 25 are maneuvered to release the seal 26, 28 which takes its place. shape and is positioned spontaneously in the groove 110, 112.

Dans le second mode de réalisation qui est représenté aux figures 5a à 8a et 5b à 8b, chaque joint 26, 28 comporte un évidement, qui est agencé en arrière de sa lèvre et qui est destiné a recevoir un anneau 27 de renfort intérieur. Cet anneau 27 de renfort intérieur est destiné à éviter l'extrusion du joint 26, 28, comme on le verra ultérieurement.In the second embodiment which is shown in FIGS. 5a to 8a and 5b to 8b each gasket 26, 28 has a recess, which is arranged behind its lip and which is intended to receive a ring 27 of internal reinforcement. This ring 27 of internal reinforcement is intended to prevent the extrusion of the seal 26, 28, as will be seen later.

L'anneau 27 est représenté plus particulièrement à la figure 10.Ring 27 is shown more particularly at figure 10 .

Avantageusement, l'anneau est réalisé en un matériau sensiblement élastique, et il comporte une portée tronconique 29 et une fente axiale 31 agencée sur sa périphérie 33 qui sont destinées à faciliter son montage, comme on le verra ultérieurement en référence aux figures 12 à 14.Advantageously, the ring is made of a substantially elastic material, and it comprises a frustoconical bearing surface 29 and an axial slot 31 arranged on its periphery 33 which are intended to facilitate its assembly, as will be seen later with reference to Figures 12 to 14 .

Avantageusement l'anneau peut comporter des rainures axiales 35 agencées sur la face intérieure 37 de sa périphérie 33.Advantageously, the ring may comprise axial grooves 35 arranged on the inner face 37 of its periphery 33.

Avantageusement, dans le mode de réalisation préféré de l'invention, l'anneau 27 est réalisé en un matériau élastomère.Advantageously, in the preferred embodiment of the invention, the ring 27 is made of an elastomeric material.

Comme on peut le voir sur les figures 1a et 5a, dans la position de repos de chaque piston, la lèvre du joint avant 26 est au contact de la périphérie du piston 18, et la lèvre du joint avant 28 est au contact de la périphérie du piston 16. Dans cette configuration, les chambres arrières d'alimentation 34, 38 étant en communication avec les chambres avant 36, 40, le joint est soumis à une pression égale sur chacune de ses faces. Les figures 1b et 5b illustrent plus particulièrement le détail de la lèvre 114 du joint avant 26 qui est au contact du piston 18.As can be seen on the figures 1a and 5a in the rest position of each piston, the lip of the front seal 26 is in contact with the periphery of the piston 18, and the lip of the front seal 28 is in contact with the periphery of the piston 16. configuration, the rear supply chambers 34, 38 being in communication with the front chambers 36, 40, the seal is subjected to equal pressure on each of its faces. The figures 1b and 5b illustrate in particular the detail of the lip 114 of the front seal 26 which is in contact with the piston 18.

Dans le second mode de réalisation de l'invention, comme on peut le voir à la figure 5a, une face arrière 118 intérieure du joint 26 est disjointe de l'anneau 27, ce qui permet la circulation du fluide hydraulique.In the second embodiment of the invention, as can be seen in figure 5a , an inner rear face 118 of the seal 26 is disjoined from the ring 27, which allows the circulation of the hydraulic fluid.

Les figures 2a et 6a représentent une position d'inhibition des moyens de communication.The Figures 2a and 6a represent a position of inhibition of the communication means.

Selon le premier mode de réalisation, comme l'illustre la figure 2a, l'avancée du piston primaire 16 a provoqué l'obturation du conduit 90 associé au piston 16 en plaquant le joint annulaire 102 contre la face arrière 94 d'épaulement du tronçon avant 54 du piston 16. Ceci produit une légère montée en pression du fluide hydraulique de freinage dans la chambre avant 36 de pression, ce qui repousse le piston secondaire 18 et provoque l'obturation du conduit 92 associé au piston 18 en plaquant le joint annulaire 104 contre la face arrière 96 d'épaulement du tronçon avant 56 du piston 18.According to the first embodiment, as illustrated by figure 2a , the advance of the primary piston 16 has caused the closure of the conduit 90 associated with the piston 16 by pressing the annular seal 102 against the rear face 94 of the shoulder of the front section 54 of the piston 16. This produces a slight rise in pressure of the hydraulic fluid for braking in the front pressure chamber 36, which pushes the secondary piston 18 and closes the conduit 92 associated with the piston 18 by pressing the annular seal 104 against the rear shoulder face 96 of the front section 56 of the piston 18.

Dans cette configuration, les faces avant des joints 28 et 26 sont soumises à une pression qui les plaque contre la périphérie des pistons respectifs 16 et 18. Les flèches de la figure 3b illustrent l'action des forces de pression sur la face avant 116 de la lèvre 114 du joint 26.In this configuration, the front faces of the seals 28 and 26 are subjected to a pressure which plates against the periphery of the respective pistons 16 and 18. The arrows of the figure 3b illustrate the action of the pressure forces on the front face 116 of the lip 114 of the gasket 26.

Selon le second mode de réalisation, comme l'illustre la figure 6a, l'avancée du piston primaire 16 a provoqué l'obturation du conduit 106 associé au piston 16, lequel conduit a avancé selon une position par rapport au joint avant 28 qui est opposée à celle qu'il occupait précédemment en position de repos du piston 16.According to the second embodiment, as illustrated by figure 6a the advance of the primary piston 16 has caused the closure of the conduit 106 associated with the piston 16, which conduit has advanced in a position relative to the front seal 28 which is opposite to that which it previously occupied in the rest position of the piston 16.

Ceci produit une légère montée en pression du fluide hydraulique de freinage dans la chambre 36 avant de pression, ce qui repousse le piston secondaire 18 et provoque l'obturation du conduit 108 associé au piston 18. Le conduit 108 associé au piston 18 avance à son tour jusqu'à une position par rapport au joint avant 26 qui est opposée à celle qu'il occupait précédemment en position de repos. Dans cette configuration, les faces avant des joints 28 et 26 sont soumises à une pression qui les plaque contre la périphérie des pistons respectifs 16 et 18.This produces a slight rise in pressure of the hydraulic brake fluid in the chamber 36 before pressure, which pushes the secondary piston 18 and causes the closure of the conduit 108 associated with the piston 18. The conduit 108 associated with the piston 18 advances to its turn to a position relative to the front seal 26 which is opposite to that previously occupied in the rest position. In this configuration, the front faces of the seals 28 and 26 are subjected to a pressure which plates them against the periphery of the respective pistons 16 and 18.

La figure 6b illustre l'action des forces de pression, représentées par des flèches, sur la face avant 116 de la lèvre 114 du joint 26. Ces forces de pression plaquent la lèvre 116 du joint 26 contre le piston 18 et plaquent la face arrière 118 intérieure du joint 26 contre l'anneau 27, garantissant ainsi une bonne étanchéité.The figure 6b illustrates the action of the pressure forces, represented by arrows, on the front face 116 of the lip 114 of the seal 26. These pressure forces press the lip 116 of the seal 26 against the piston 18 and press the inner rear face 118 of the seal 26 against the ring 27, thus ensuring a good seal.

Les figures 3a et 7a représentent une position d'application d'un effort de freinage par les pistons 16 et 18.The figures 3a and 7a represent a position of application of a braking force by the pistons 16 and 18.

L'avancée des pistons primaires 16 et 18 a provoqué l'obturation des conduits 90, 92 associés au premier mode de réalisation et des conduits 106 108 associés au second mode de réalisation. Chacun de ces conduits a avancé selon une position par rapport au joint avant respectif 26, 28 qui est opposée à celle qu'il occupait précédemment en position de repos. Le fluide hydraulique de freinage est sous pression dans les deux chambres avant 36 et 40.The advance of the primary pistons 16 and 18 caused the closure of the conduits 90, 92 associated with the first embodiment and the conduits 106 associated with the second embodiment. Each of these ducts has advanced in a position relative to the respective front seal 26, 28 which is opposite to that which it previously occupied in the rest position. The hydraulic brake fluid is under pressure in the two front chambers 36 and 40.

Dans cette configuration, les faces avant des joints 28 et 26 sont soumises à une pression qui les plaque contre la périphérie des pistons respectifs 16 et 18. Les flèches de la figure 3b illustrent l'action des forces de pression sur la face avant 116 de la lèvre 114 du joint 26 associé au premier mode de réalisation. La figure 7b illustre l'action des forces de pression, représentées par des flèches, sur la face avant 116 de la lèvre 114 du joint 26 associé au second mode de réalisation. Ces forces de pression plaquent la lèvre 116 du joint 26 contre le piston 18 et plaquent la face arrière 118 intérieure du joint 26 contre l'anneau 27, garantissant ainsi une bonne étanchéité.In this configuration, the front faces of the seals 28 and 26 are subjected to a pressure which plates against the periphery of the respective pistons 16 and 18. The arrows of the figure 3b illustrate the action of the pressure forces on the front face 116 of the lip 114 of the seal 26 associated with the first embodiment. The figure 7b illustrates the action of the pressure forces, represented by arrows, on the front face 116 of the lip 114 of the seal 26 associated with the second embodiment. These Pressure forces press the lip 116 of the gasket 26 against the piston 18 and press the inner back face 118 of the gasket 26 against the ring 27, thus ensuring a good seal.

Les figures 4a et 8a représentent une position de réalimentation des chambres avant 36, 40 par les conduits radiaux 42, 48 et les réservoirs associés (non représentés) lorsque le conducteur relâche son effort sur l'extrémité 19 du piston primaire 16.The Figures 4a and 8a represent a restoring position of the front chambers 36, 40 by the radial conduits 42, 48 and the associated tanks (not shown) when the driver releases his force on the end 19 of the primary piston 16.

Dans cette configuration, les deux pistons 16 et 18 reculent rapidement et il se crée une dépression dans les chambres avant de pression primaire 36 et secondaire 40. Cette dépression soulève les lèvres des joints 26 et 28.In this configuration, the two pistons 16 and 18 retreat rapidly and there is a depression in the front chambers of primary pressure 36 and secondary 40. This depression raises the lips of the seals 26 and 28.

Comme on peut le voir par exemple aux figures 4b et 8b, les forces de dépression, représentées par des flèches, tendent à décoller la lèvre 114 du joint d'étanchéité 26 ce qui permet au fluide hydraulique de cheminer du conduit 48 vers la chambre avant de pression secondaire 40 en circulant entre l'alésage 14 et la périphérie du piston 18.As can be seen for example in Figures 4b and 8b , the depression forces, represented by arrows, tend to detach the lip 114 of the seal 26 which allows the hydraulic fluid to travel from the conduit 48 to the secondary chamber before secondary pressure 40 by circulating between the bore 14 and the periphery of the piston 18.

Dans le cas particulier du second mode de réalisation de l'invention, représenté à la figure 8b, les forces de dépression décollent la lèvre 116 du piston 18 et décollent la face arrière 118 intérieure du joint 26 de l'anneau 27, ce qui permet plus particulièrement au fluide hydraulique de cheminer du conduit 48 vers la chambre avant de pression secondaire 40 en circulant entre la face arrière 118 du joint 26 et l'anneau 27.In the particular case of the second embodiment of the invention, shown in FIG. figure 8b , the vacuum forces take off the lip 116 of the piston 18 and take off the inner rear face 118 of the seal 26 of the ring 27, which more particularly allows the hydraulic fluid to flow from the duct 48 to the front secondary pressure chamber 40 in flowing between the rear face 118 of the gasket 26 and the ring 27.

Dans les deux modes de réalisation de l'invention, comme l'illustrent les figures 1a à 9a, le corps 12 comporte de préférence une paire avant de portées annulaires 120, 122 qui sont agencées de part et d'autre du joint d'étanchéité avant 26 associé au piston 18, et une paire avant de portées annulaires 124, 126 qui sont agencées de part et d'autre du joint d'étanchéité avant 28 associé au piston 16.In both embodiments of the invention, as illustrated by the Figures 1a to 9a , the body 12 preferably comprises a pair of annular bearing surfaces 120, 122 which are arranged on either side of the front seal 26 associated with the piston 18, and a front pair of annular bearings 124, 126 which are arranged on either side of the front seal 28 associated with the piston 16.

Ces portées 120, 122, 124, 126 permettent le guidage des pistons 16, 18 dans l'alésage 14. Chacune de ces portées annulaires 120, 122, 124, 126 comporte au moins une rainure 128 de circulation du fluide hydraulique. Cette configuration permet de proposer un guidage précis du piston 16, 18 tout en permettant la réalimentation du conduit radial 42, 48 avec un débit satisfaisant.These bearing surfaces 120, 122, 124, 126 allow the guiding of the pistons 16, 18 in the bore 14. Each of these annular bearing surfaces 120, 122, 124, 126 comprises at least one groove 128 for circulating the hydraulic fluid. This configuration makes it possible to provide precise guidance of the piston 16, 18 while allowing the supply of the radial duct 42, 48 with a satisfactory flow rate.

L'anneau 27 permet avantageusement d'éviter l'extrusion du joint d'étanchéité avant 28 dans l'au moins une rainure 128.The ring 27 advantageously avoids the extrusion of the front seal 28 in the at least one groove 128.

De préférence, comme l'illustre plus précisément la figure 9b, les portées annulaires 120, 122 comportent une pluralité de rainures hélicoïdales 124.Preferably, as is more specifically illustrated by figure 9b the annular bearing surfaces 120, 122 comprise a plurality of helical grooves 124.

Par ailleurs, comme l'illustrent les figures 1a à 8a, le moyen d'étanchéité arrière 30, 32 est constitué d'un joint d'étanchéité arrière 30, 32 qui est monté dans une gorge 130, 132 du corps 12 et dont une lèvre périphérique intérieure est agencée au contact du piston 16, 18 associé.Moreover, as illustrated by Figures 1a to 8a , the rear sealing means 30, 32 consists of a rear seal 30, 32 which is mounted in a groove 130, 132 of the body 12 and of which an inner peripheral lip is arranged in contact with the piston 16, 18 associated.

Par ailleurs, comme l'illustrent les figures 1a à 9a, le corps comporte une paire arrière de portées annulaires 134, 136 qui sont agencées de part et d'autre du joint d'étanchéité arrière 30 associé au piston 18 et une paire arrière de portées annulaires 138, 140 qui sont agencées de part et d'autre du joint d'étanchéité arrière 32 associé au piston 16. Ces portées 134, 136, 138, 140 permettent le guidage des pistons 16, 18 associés dans l'alésage 14.Moreover, as illustrated by Figures 1a to 9a , the body comprises a rear pair of annular bearing surfaces 134, 136 which are arranged on either side of the rear seal 30 associated with the piston 18 and a rear pair of annular bearing surfaces 138, 140 which are arranged on both sides. other of the rear seal 32 associated with the piston 16. These bearing surfaces 134, 136, 138, 140 allow the guide of the pistons 16, 18 associated in the bore 14.

Par ailleurs, dans chacun des modes de réalisation, les moyens de butée des pistons 16, 18 comportent à l'extrémité de chaque piston un anneau élastique extérieur 142, 144 qui est susceptible, dans la position de repos du piston 16, 18, de venir au contact d'une face d'épaulement avant de la portée annulaire 124, 120 avant qui fait partie de la paire avant de portées annulaires.Furthermore, in each of the embodiments, the stop means of the pistons 16, 18 comprise at the end of each piston an external elastic ring 142, 144 which is capable, in the rest position of the piston 16, 18, of come into contact with a shoulder face before the annular bearing surface 124, 120 which is part of the front pair of annular bearings.

Les figures 12 à 14 illustrent trois étapes successives du montage dans le corps 12 de l'anneau 27 de renfort associé au joint d'étanchéité 26 du second mode de réalisation.The Figures 12 to 14 illustrate three successive steps of assembly in the body 12 of the reinforcement ring 27 associated with the seal 26 of the second embodiment.

Pour le montage on utilise trois outils 150, 160 et 170.For assembly, three tools 150, 160 and 170 are used.

L'outil 150 est tubulaire et comporte un tronçon avant 152 qui est sensiblement du diamètre de l'alésage 14, et un tronçon arrière 154 qui est sensiblement d'un diamètre égal au diamètre intérieur de l'anneau de renfort 27 comprimé. L'outil 150 comporte un chanfrein tronconique 156 à l'extrémité arrière de son tronçon avant 152. La longueur du tronçon avant 152 est prévue pour que l'extrémité arrière du tronçon avant 152 coïncide axialement sensiblement avec la gorge 112.The tool 150 is tubular and has a front section 152 which is substantially the diameter of the bore 14, and a rear section 154 which is substantially of a diameter equal to the inner diameter of the compressed reinforcement ring 27. The tool 150 comprises a frustoconical chamfer 156 at the rear end of its front section 152. The length of the front section 152 is provided so that the rear end of the front section 152 coincides axially substantially with the groove 112.

L'outil 160 est sensiblement tubulaire et comporte un tronçon avant 162 qui est sensiblement du diamètre moyen de l'anneau de renfort 27 comprimé. L'outil 160 comporte un chanfrein tronconique 166 à l'extrémité avant de son tronçon avant 162. Il comporte aussi un tronçon arrière 164 formant molette de préhensidn, d'un diamètre supérieur au tronçon avant 162.The tool 160 is substantially tubular and has a front section 162 which is substantially the average diameter of the compressed reinforcement ring 27. The tool 160 has a frustoconical chamfer 166 at the front end of its front section 162. It also comprises a rear section 164 forming a prehensid wheel, with a larger diameter than the front section 162.

L'outil 170 est sensiblement tubulaire et comporte un tronçon avant 172 qui est sensiblement d'un diamètre intérieur égal au diamètre extérieur de l'anneau de renfort 27 comprimé. Il comporte aussi un tronçon arrière 174 formant molette de préhension, d'un diamètre supérieur au tronçon avant 172.The tool 170 is substantially tubular and has a front section 172 which is substantially of an inner diameter equal to the outer diameter of the compressed reinforcement ring 27. It also comprises a rear section 174 forming a grip wheel, with a larger diameter than the front section 172.

L'anneau 27 est comprimé puis enfilé sur le tronçon arrière 154 de l'outil 150. Puis l'outil 160 est enfilé suivant une position axiale intermédiaire dans l'outil 170 et sur l'outil 150. L'ensemble des trois outils 150, 160, 170 et de l'anneau 27 est introduit dans l'alésage 14 du corps 12. L'anneau 27 alors est tenu axialement par l'extrémité du tronçon avant 162 de l'outil 160, et il est maintenu radialement par le tronçon avant 172 de l'outil 170, avec un jeu axial J entre l'anneau 27 et le tronçon avant 152 de l'outil 150, comme représenté à la figure 12.The ring 27 is compressed and then threaded onto the rear section 154 of the tool 150. Then the tool 160 is threaded in an intermediate axial position in the tool 170 and the tool 150. The set of three tools 150 160, 170 and the ring 27 is introduced into the bore 14 of the body 12. The ring 27 is then held axially by the end of the front section 162 of the tool 160, and is held radially by the front section 172 of the tool 170, with an axial clearance J between the ring 27 and the front section 152 of the tool 150, as shown in FIG. figure 12 .

Puis, comme l'illustre la figure 13, l'outil 160 est repoussé vers l'avant de manière à réduire le jeu J. L'anneau 27 s'échappe alors du tronçon avant 172 et reprend spontanément sa forme en appui sur le chanfrein tronconique 166 de l'outil 160.Then, as illustrated by figure 13 , the tool 160 is pushed forward so as to reduce the clearance J. The ring 27 then escapes from the front section 172 and spontaneously resumes its shape bearing on the frustoconical chamfer 166 of the tool 160.

Enfin comme l'illustre la figure 14, l'ensemble des trois outils 150, 160, 170 est ôté de l'alésage 14 du corps 12, le chanfrein tronconique 156 agencé à l'extrémité arrière de son tronçon avant 152 permettant le passage de l'outil 150 sans destruction de l'anneau 27 de renfort.Finally, as illustrated by figure 14 , all three tools 150, 160, 170 is removed from the bore 14 of the body 12, the frustoconical chamfer 156 arranged at the rear end of its front section 152 allowing the passage of the tool 150 without destruction of the reinforcement ring 27.

L'invention permet donc de disposer d'un maître-cylindre muni d'une étanchéité d'une grande fiabilité.The invention therefore makes it possible to have a master cylinder provided with a seal of high reliability.

Claims (14)

  1. Brake master cylinder (10) for a motor vehicle, of the type which comprises an essentially axial body (12) inside a bore (14) of which is slideably mounted at least one axial piston (16, 18) which is capable of being actuated by a driver of the vehicle between a rear position of rest and a forward position of application of a braking force, and which is returned elastically to its rear position of rest against a stop formed in the body (12), of the type in which the bore (14) comprises two sealing means, front (26, 28) and rear (30, 32), which are interposed between the piston (16, 18) and the bore (14), the front sealing means (26, 28) delimiting, in the bore (14), a rear supply chamber (34, 38) and a front pressure chamber (36, 40), of the type in which the body (12) comprises a radial supply duct (42, 48) which connects an external reservoir of hydraulic fluid to the rear supply chamber (34, 38) and which opens between the two sealing means (26, 28, 30, 32), of the type in which the body (12) has a drilling (50, 52) for supplying a braking circuit which opens into the front pressure chamber (36, 40), of the type which comprises means for placing the front pressure chamber (36, 40) and the rear supply chamber (34, 38) in communication, which means are capable of being inhibited by the piston (16, 18) when it is moved axially forward towards its position of application in order to isolate the front pressure chamber (36, 40) from the rear supply chamber (34, 38) and thus allow a braking pressure to become established in the front pressure chamber (36, 40),
    characterized in that the front sealing means (26, 28) comprises a front seal (26, 28) which is mounted in a groove (110, 112) of the body (12), and of which an interior peripheral lip, arranged in contact with the piston (16, 18), is capable of lifting off the piston (16, 18) when it returns from its position of application to its position of rest so as to allow the hydraulic fluid, by flowing between the bore (14) and the piston (16, 18), to resupply the front pressure chamber (36, 40) from the radial supply duct (42, 48) and from the reservoir and in that the body (12) comprises a front pair of annular bearing surfaces (120, 122, 124, 126) which are arranged on each side of the front seal (26, 28) to guide the piston (16, 18) in the bore (14) and which comprise a number of helical channels (128) along which the hydraulic fluid can flow.
  2. Master cylinder (10) according to claim 1, characterized in that the piston (16, 18) is one-piece, in particular, tubular, and has at least one duct (106, 108) a first end of which opens into the front pressure chamber (36, 40) and a second end of which opens into the periphery of the piston (16, 18) in such a way as to communicate with the supply chamber (34, 38) when the piston (16, 18) is in the position of rest so as to form the means of communication and so as to communicate with the front pressure chamber (36, 40) when the piston (16, 18) is in the position of application so as to inhibit the means of communication.
  3. Master cylinder (10) according to the preceding claim, characterized in that the seal (26, 28) comprises an interior reinforcing ring (27) which is intended to prevent the seal (26, 28) from becoming extruded.
  4. Master cylinder (10) according to the preceding claim, characterized in that the ring (27) is made of a fairly elastic material, in that it comprises a frustoconical bearing surface (29) and an axial slot (31) arranged on its periphery (33) and which are intended to make it easier to fit.
  5. Master cylinder according to the preceding claim, characterized in that the ring (27) comprises at least one axial slot arranged on the interior face (37) of its periphery (33).
  6. Master cylinder (10) according to one of Claims 3 to 5, characterized in that the ring (27) is made of an elastomeric material.
  7. Master cylinder (10) according to Claim 1, characterized in that the piston (16, 18) comprises a front portion (54, 56) and a rear portion (58, 60) which are tubular and of the same outside diameter (D), a rear bearing surface (62, 64) of the front portion (54, 56) sliding in a bore (66, 68) of the rear portion (58, 60), and in that retaining means (78, 80, 82, 84) and elastic urging means (86, 88) are interposed between a rear face (70, 72) of the front portion (54, 56) and the closed end (74, 76) of the bore (66, 68) of the rear portion (58, 60).
  8. Master cylinder (10) according to the preceding claim, characterized in that the front portion (54, 56) comprises at least one duct (90, 92) a first end of which opens into the front pressure chamber (36, 40) and a second end of which opens into the periphery of the rear bearing surface (62, 64) between a shoulder rear face (94, 96) of the front portion (54, 56) and a shoulder front face (98, 100) of the rear portion (58, 60) to form a moving valve which, when the piston (16, 18) is in the position of rest, opens into the supply chamber (34, 38) and constitutes the means of communication.
  9. Master cylinder (10) according to the preceding claim, characterized in that the shoulder front face (98, 100) of the rear portion has an annular seal (102, 104).
  10. Master cylinder (10) according to any one of the preceding claims, characterized in that the rear sealing means (30, 32) consists of a rear seal (30, 32) which is mounted in a groove (130, 132) of the body (12) and of which an interior peripheral lip is arranged in contact with the piston (16, 18).
  11. Brake master cylinder (10) according to the preceding claim, characterized in that the body (12) comprises a rear pair of annular bearing surfaces (134, 136, 138, 140) which are arranged one on each side of the rear seal (30, 32) to guide the piston (16, 18) in the bore (14).
  12. Master cylinder (10) according to any one of Claims 1 to 11, characterized in that the piston (16, 18) at its end comprises an external elastic ring (142, 144) which is capable, when the piston (16, 18) is in the position of rest, of coming into contact with a front shoulder face of the front annular bearing surface (120, 124) of the front pair of annular bearing surfaces forming a stop.
  13. Master cylinder (10) according to any one of the preceding claims, characterized in that the piston (16, 18) is elastically returned to its rear position of rest by a spring (20, 24).
  14. Master cylinder (10) according to any one of the preceding claims, characterized in that it is a master cylinder of the "tandem" type which comprises, from the rear forward, two pistons primary (16), (18) and secondary, which delimit in the bore of the body primary (34) and secondary (38) supply chambers and primary (36) and secondary (40) pressure chambers, the primary piston (16) being returned elastically to its rear position of rest by a spring (24) bearing between a rear face (61) of the secondary piston (18) and a front face of the primary piston (16).
EP02704796A 2001-02-09 2002-01-25 Master cylinder comprising a fluid and replenishing seal Expired - Lifetime EP1360100B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0101897 2001-02-09
FR0101897A FR2820701B1 (en) 2001-02-09 2001-02-09 MASTER CYLINDER COMPRISING A SEAL AND REALIMENTATION
PCT/FR2002/000324 WO2002064410A1 (en) 2001-02-09 2002-01-25 Master cylinder comprising a fluid and replenishing seal

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EP1360100A1 EP1360100A1 (en) 2003-11-12
EP1360100B1 true EP1360100B1 (en) 2010-06-30

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EP02704796A Expired - Lifetime EP1360100B1 (en) 2001-02-09 2002-01-25 Master cylinder comprising a fluid and replenishing seal

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US (1) US6848257B2 (en)
EP (1) EP1360100B1 (en)
JP (1) JP4209682B2 (en)
KR (1) KR20020089567A (en)
CN (1) CN1288017C (en)
AT (1) ATE472448T1 (en)
BR (1) BR0204176B1 (en)
DE (1) DE60236847D1 (en)
FR (1) FR2820701B1 (en)
WO (1) WO2002064410A1 (en)

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Publication number Publication date
EP1360100A1 (en) 2003-11-12
US20040079078A1 (en) 2004-04-29
BR0204176A (en) 2003-01-14
CN1288017C (en) 2006-12-06
FR2820701A1 (en) 2002-08-16
CN1458890A (en) 2003-11-26
JP4209682B2 (en) 2009-01-14
JP2004521799A (en) 2004-07-22
ATE472448T1 (en) 2010-07-15
BR0204176B1 (en) 2010-10-19
DE60236847D1 (en) 2010-08-12
WO2002064410A1 (en) 2002-08-22
KR20020089567A (en) 2002-11-29
FR2820701B1 (en) 2003-04-18
US6848257B2 (en) 2005-02-01

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